WO2023117961A1 - Hydraulic valve spool through which a fluid can flow, bidirectional control valve, and method - Google Patents

Abstract

The invention relates to a hydraulic valve spool (14a-b) through which a fluid can flow, in particular for a control valve (10a-b) for controlling the damping characteristics of shock absorbers, comprising at least one hydraulic combinational valve (12a-b) has at least a first control port (16a-b), at least a second control port (18a-b), at least one inlet (20a-b, 36a-b) and at least one outlet (22a-b, 40b) that can be alternately opened to at least the inlet (20a-b).

Description

13.12.2022

Flow-through hydraulic valve spool, bi-directional control valve and method

State of the art

The invention relates to a valve slide according to claim 1, a control valve according to the preamble of claim 16, a vehicle according to claim 19 and a method according to claim 20.

It has been suggested that closed volumes that are displaced or filled by movement of a valve spool are provided with large leakages in bearing gaps to accommodate the excess or deficient volumes.

The object of the invention is in particular to provide a generic device with advantageous damping properties. The object is achieved according to the invention by the features of claims 1, 16, 19 and 20, while advantageous configurations and developments of the invention can be found in the dependent claims.

Advantages of the Invention

A hydraulic valve slide through which flow is possible, in particular for a control valve for regulating damping characteristics of shock absorbers, with at least one hydraulic linkage valve for influencing flow through the valve slide, the hydraulic linkage valve having at least one first control port, at least one second control port, at least one input and at least one Exit, preferably at least two outputs, which / r are interchangeably openable at least to the input is proposed. This allows advantageous damping properties to be achieved. A damping characteristic for shock absorbers can advantageously be achieved which at the same time has high dynamics and low overall leakage. A conflict of objectives between dynamics and leakage, which occurs with known control valves (there, high dynamics generally means high leakage), can advantageously be resolved by the invention. Advantageously, due to a low overall leakage, regulation can be made possible even at low damper speeds, in particular by being able to achieve a particularly low opening point of the control valve. The total leakage can advantageously be optimized independently of the dynamics to be achieved, for example by significantly reducing a leakage with the same manufacturing tolerance (functional advantage) or by advantageously expanding manufacturing tolerances without creating particularly disadvantageous effects (cost advantage).

In particular, the valve spool forms a component of the control valve for controlling the damping characteristics of shock absorbers. In particular, the valve slide separates a pressure side of a shock absorber that has the control valve from a non-pressurized side of the shock absorber. In particular, the pressure side can change depending on whether a tensile force or a pressure force is present. Opening the separation between the pressure side and the non-pressurized side by the valve spool causes damping through an oil flow. In particular, the valve slide includes hydraulic active surfaces. In particular, the valve slide has at least one hydraulic effective surface and at least one additional hydraulic effective surface, the hydraulic effective surface and the additional hydraulic effective surface(s) being arranged relative to one another on the valve slide in such a way that, in particular during a damping process , Counteract each other hydraulically, and in particular on the hydraulic active surfaces to be damped train or Attack compressive forces of the shock absorber. In particular, a fluid, for example an oil, preferably a hydraulic oil, can flow through the valve slide at least in sections. In particular, the ability of the valve slide to flow through means that oil, in particular hydraulic oil, can be pumped back and forth between a pressurized fluid reservoir of the control valve and an unpressurized (pressurized fluid) tank of the shock absorber. The assignment of the unpressurized area, ie the unpressurized (pressurized fluid) tank, changes in particular depending on the direction of flow. This switchover is advantageously achieved essentially without significant leakage losses and without an undesired build-up of significant opposing forces. As a result, high switching dynamics of the control valve can advantageously be achieved with chassis control already starting at low chassis vibrations. In particular, the valve slide can be flown through in both directions. In particular, the valve slide has at least four different flow paths. In particular, the hydraulic linkage valve is provided for influencing a flow of at least two of the four flow paths, preferably of all four flow paths. In particular, the linkage valve is integrated into the valve slide. In particular, the linking valve is completely surrounded by the valve slide. In particular, at least one of the control connections, preferably all of the control connections, forms inputs of the linking valve at the same time. In particular, the hydraulic pressures present at the control connections of the linkage valve control the linkage valve, in particular the valve position of the linkage valve. In particular, the linkage valve has no electronic, magnetic and/or mechanical control. In particular, the linkage valve is controlled/actuated purely fluidically. In particular, the linking valve has the pressure fluid flowing through it. In particular, the control connections can/are controlled by pressure signals. In particular, the input can coincide with at least one of the control connections. In particular, the linking valve can have two inputs, with both inputs coinciding with different control connections can. Alternatively, it is conceivable that at least one input is formed separately from a control connection and/or that at least one control connection does not form an input into which a fluid flowing through the logic valve can enter.

It is also proposed that the hydraulic valve slide through which flow can take place has a sealing surface intended to sit tightly on a valve seat of the control valve, the first control connection being hydraulically connected to a first side of the valve slide, the second control connection being hydraulically connected to a second side of the valve slide , and wherein the two sides to which the control connections are hydraulically connected are arranged on the valve slide in such a way that the first side and the second side can be sealed off from one another by the sealing surface. This allows advantageous damping properties to be achieved. In this way, it is advantageously possible to control the linkage valve, in particular a connection to the outlet of the linkage valve, as a function of the pressures applied externally on both sides. In particular, the sides of the valve spool are hydraulically isolated from one another when the valve spool is sealingly seated on the valve seat. In particular, one of the control connections is always arranged on a pressure side of the valve slide, while the other of the control connections is arranged on a pressure-free side of the valve slide. In particular, the opening point of the shock absorber is the point at which the valve spool is lifted from the valve seat. The valve slide is intended to generate damping of an applied tensile or compressive force depending on its open position. When an applied tensile or compressive force is large enough to lift the valve spool from the valve seat, a pressurized fluid flows between the two sides, creating a dampening of the applied tensile or compressive forces. The control valve is provided for adjusting the damping force/damping hardness by influencing the opening movement of the valve slide, for example by means of magnetic fields. The valve spool is one with a magnet armature electromagnet connected. The electromagnet is provided to generate a force opposing an opening movement of the valve slide. “Provided” should be understood to mean, in particular, specially programmed, designed and/or equipped. In particular, the sealing surface is arranged on a side of the valve slide pointing away from the electromagnet, with a reverse configuration also being generally conceivable. The fact that an object is provided for a specific function is to be understood in particular to mean that the object fulfills and/or executes this specific function in at least one application and/or operating state.

In addition, it is proposed that the output, which preferably differs from the control connections, is hydraulically connected to a third side of the valve slide, which is arranged opposite the sealing surface as seen in a planned direction of movement of the valve slide. This allows advantageous damping properties to be achieved. Advantageously, a controllable (at least partially axial) flow through the valve slide can be achieved. In particular, the outlet that is different from the control connections is open to a side of the valve slide that is arranged opposite the sealing surface in the axial direction of the valve slide. In particular, the outlet is connected either to a hydraulic effective surface, in particular a hydraulic effective surface which is different from the hydraulic effective surfaces on which chassis vibrations are exerted, or to the pressure fluid reservoir.

If the hydraulic linkage valve is designed as a dual-pressure valve, which is intended in particular to connect the input to which the control port with the lower pressure is assigned, in particular the control port of the two control ports at which a lower pressure is present, to that, in particular from the control ports Different, outlet, preferably the outlet of the two-pressure valve to open and / or keep open, advantageous damping properties can be achieved. Targeted control of the flow through the valve slide can be advantageous be reached. This advantageously enables an exchange between the pressure fluid reservoir of the control valve and the unpressurized (pressure fluid) tank of the shock absorber that is as resistance-free as possible. Leakage can advantageously be kept low while enabling high dynamics. The valve slide has in particular at least one flow channel with at least one branch, with each branch path preferably forming one of the four through-flow paths. A first sub-channel of the flow channel, a second sub-channel of the flow channel and a third sub-channel of the flow channel meet at the junction. The first sub-channel of the flow channel and the second sub-channel of the flow channel preferably together form the first flow path of the valve slide. The first sub-channel of the flow channel and the third sub-channel of the flow channel preferably together form the second flow path of the valve slide. The two-pressure valve is arranged in particular in the branching of the flow channel and is intended to open and/or keep open the first sub-channel to that of the two further sub-channels at which a lower pressure is present. The two-pressure valve preferably closes the first sub-channel to that of the two other sub-channels with the higher pressure at the same time.

Furthermore, it is proposed that the outlet of the two-pressure valve is hydraulically connected to an area of the valve slide that at least partially delimits the pressure fluid reservoir of the control valve, with the pressure fluid reservoir being provided in particular for the purpose, when the valve slide is moved, via at least one through the two-pressure valve controlled flow path to be charged and / or emptied. This allows advantageous damping properties to be achieved. Targeted regulation of the flow through the valve slide can advantageously be achieved. This advantageously enables an exchange between the pressure fluid reservoir of the control valve and the unpressurized (pressure fluid) tank of the shock absorber that is as resistance-free as possible. In particular, the two-pressure valve ensures that the flow path always opens into the currently unpressurized (pressurized fluid) tank and thus the filling and emptying of the pressurized fluid reservoir runs at least essentially without resistance when the valve slide moves.

If the hydraulic linkage valve is designed as a shuttle valve, which is provided in particular to connect the input to which the control port with the higher pressure is assigned, in particular the control port of the two control ports at which a higher pressure is present, to that, in particular from the control ports Different, output, preferably the output of the shuttle valve to open and / or keep open, advantageous damping properties can be achieved. Targeted regulation of the flow through the valve slide can advantageously be achieved. This advantageously enables the most efficient and/or dynamic transmission of forces, in particular shock absorber tensile forces and/or compressive forces, to the hydraulic effective surface of the valve slide, which is intended to generate a counterforce to these forces. In particular, the hydraulic effective area is larger than the additional hydraulic effective area(s), in particular regardless of whether additional connectable hydraulic sub-effective areas are added to the hydraulic effective area or not. The valve slide has in particular at least one further flow channel with at least one branch, with each branch path preferably forming one of the four through-flow paths. A first sub-channel of the further flow channel, a second sub-channel of the further flow channel and a third sub-channel of the further flow channel meet at the junction. The first sub-channel of the further flow channel and the second sub-channel of the further flow channel preferably together form the third flow path of the valve slide. The first sub-channel of the further flow channel and the third sub-channel of the further flow channel preferably together form the fourth flow path of the valve slide off. The shuttle valve is arranged in particular in the branching of the further flow channel and is intended to open and/or keep open the first sub-channel to that of the two further sub-channels at which a higher pressure is present. The two-pressure valve preferably closes the first sub-channel to that of the two other sub-channels with the lower pressure at the same time. The shuttle valve is provided in particular for hydraulically separating the currently unpressurized side from the first sub-channel of the further flow channel. In particular, the shuttle valve ensures that a flow path of the outlet of the further flow channel always opens into the currently pressurized tank and thus the pressure also on the (upper) hydraulic effective surface, which is intended in particular to create a counterforce to the shock absorber tensile forces and/or - To generate compressive forces is present.

As a result, it is proposed that the output of the shuttle valve is hydraulically connected to a hydraulic effective area, in particular of the valve slide, which is connected to a further hydraulic active area, in particular of the valve slide, which is formed on the side of the valve slide to which the shuttle valve, in particular the Control connection of the shuttle valve, is currently open, opposite. This allows advantageous damping properties to be achieved. This advantageously enables the most efficient and/or dynamic transmission of forces, in particular shock absorber tensile forces and/or compressive forces, to the hydraulic effective surface of the valve slide, which is intended to generate a counterforce to these forces.

In addition, it is proposed that the opposing hydraulic effective areas are of different sizes. This allows advantageous damping properties to be achieved. A pressure-dependent force difference can advantageously be achieved between the opposite sides of the valve slide. In particular, the hydraulic effective area is larger than each of the other hydraulic effective areas. In particular, the hydraulic effective area, preferably a total of all hydraulic partial effective areas of the hydraulic effective area by at least 3%, preferably by at least 5%, advantageously by at least 10%, preferably by at least 15% and preferably by at most 25% greater than the respective opposite additional hydraulic effective area on the pressure or train side.

In addition, it is proposed that the hydraulic valve spool through which flow can take place has at least one further hydraulic linkage valve, which in particular differs from the hydraulic linkage valve in a functional principle, for influencing flow through the valve spool, with the further hydraulic linkage valve having at least one first control connection and at least one second control connection and in particular at least one output which can be opened to at least one of the control connections in an exchangeable manner. This allows advantageous damping properties to be achieved. As a result, flow properties of the valve slide that are advantageous for damping can be achieved. In particular, the hydraulic linkage valve and the further hydraulic linkage valve have different outlets, which are in particular configured separately from one another and/or are sealed from one another.

If the hydraulic linkage valve is designed as a dual-pressure valve and the other hydraulic linkage valve is designed as a shuttle valve, high dynamics can advantageously be achieved with low leakage at the same time. In particular, the two-pressure valve and the shuttle valve are each housed by the valve slide. In particular, the two-pressure valve and the shuttle valve are designed separately from one another. In particular, the respective movement axes of the valve elements of the dual-pressure valve and shuttle valve run in directions that are not parallel to one another.

If, in addition, the hydraulic linkage valve corresponds to the flow channel at least partially formed by the valve slide (one of the outputs) and the further hydraulic linkage valve is assigned to the further flow channel (other of the outlets) at least partially formed by the valve slide, with the two flow channels being formed completely separate from one another, in particular without any connection to one another, high dynamics can advantageously be achieved with low leakage at the same time be reached.

Alternatively, it is proposed that the hydraulic linkage valve be designed as a single valve, which has at least one additional outlet and which combines the function of a shuttle valve with the function of a dual-pressure valve in one valve. As a result, complexity can advantageously be further reduced, in particular by further reducing the number of parts. Advantageously, costs can be kept low as a result. In particular, in this case the valve slide is free of additional valves, such as additional shuttle valves or additional two-pressure valves. In particular, the individual valve is arranged in the first flow channel and in the second flow channel of the valve slide at the same time.

Furthermore, it is proposed that the individual valve is designed as a 4/2 shuttle valve, which is provided for the purpose of connecting the input, which is assigned to the control connection of the two control connections, at which a higher pressure is present, in particular in relative terms, to the Output, in particular to the output of the linkage valve, which is hydraulically connected to the hydraulic active surface, to open and / or to keep open and at the same time the input, which is assigned to the control connection of the two control connections, at which a pressure, in particular relatively speaking, is lower applied to the other output, in particular to the output of the linking valve, which is hydraulically connected to the pressure fluid reservoir to open and / or keep open. As a result, the function of a shuttle valve and a two-pressure valve can advantageously be combined in a single valve. As a result, complexity and costs can advantageously be reduced. In addition, it is proposed that the hydraulic linking valve designed as a 4/2 shuttle valve has a linking valve valve slide through which flow can flow at least in sections. As a result, a high degree of compactness can advantageously be achieved. In addition, an advantageous valve design can be achieved which is particularly suitable for combining the functions of a two-pressure valve and a shuttle valve in a single valve. In particular, the linkage valve slide has a flow channel, in particular an internal flow channel, which extends over at least a large part of a longitudinal extent of the linkage valve slide.

In addition, it is proposed that the hydraulic valve slide through which flow can take place has an orifice-free design, in particular apart from the hydraulic linkage valve and/or apart from the further hydraulic linkage valve. As a result, a complexity and in particular a number of components can advantageously be kept low. An “aperture” is to be understood in particular as a local flow resistance element with an abrupt narrowing of the cross section, in which the ratio of length to diameter is relatively small, preferably less than 1.5.

Furthermore, a preferably proportional, bidirectional control valve is proposed for controlling damping characteristics, in particular of shock absorbers, with the hydraulic valve slide through which flow can take place. As a result, advantageous damping properties and/or damping characteristics can be provided. In particular, the bidirectional control valve is provided for controlling the damping characteristics in two directions, preferably in a tension direction and in a compression direction. A “proportional bidirectional control valve” should be understood to mean, in particular, a bidirectional control valve which is intended to control a damping force, preferably of a shock absorber, in a manner proportional to the current. In particular, the bidirectional control valve provided that, in the case of a bidirectional flow, equalization of a fluid volume is always conducted into a space with a lower pressure, while at the same time equalization of the fluid volume with a space of higher pressure is blocked. In a conventional design with orifices, this would mean that, in contrast to a unidirectional control valve, twice the number of orifices that would take up space would be required. Due to the design according to the invention, installation space, the number of components and thus costs can be kept low.

In addition, it is proposed that the bidirectional control valve be specially designed to achieve controllability of a pressure drop at the valve slide from a volume flow of less than 10 l/min, preferably less than 5 l/min and preferably less than 2 l/min. As a result, advantageous damping properties/damping characteristics can be achieved. In particular, an opening point/break point of the bidirectional control valve is below 10 l/min, preferably below 5 l/min and preferably below 2 l/min

Furthermore, it is proposed that the bidirectional control valve have a first tank, in particular for a shock absorber rebound stage, and a second tank that can be separated from the first tank by the valve slide, in particular for a shock absorber compression stage, and a volume-variable and separated from pressure fluid reservoir formed in the tanks, which can be partially filled and/or partially emptied by flowing through the valve slide, with the hydraulic linkage valve designed as a two-pressure valve being provided for the purpose of automatically and dynamically establishing a valve slide flow connection between the pressure fluid reservoir and only that of the two tanks which currently has a lower pressure load, in particular which is currently depressurized. As a result, advantageous damping properties/damping characteristics can be achieved, which preferably allow high dynamics with low leakage. In particular, the first tank as a first chamber of a piston rod of a shock absorber is formed. In particular, the second tank is designed as a second chamber of the piston rod of the shock absorber.

In addition, a vehicle with the bidirectional control valve is proposed, which has an advantageously comfortable chassis.

In addition, a method for an automatic setting of instantaneous flow directions through flow-through valve slides, the instantaneous flow directions from the dual-pressure valve, in particular at least partially integrated in the valve slide, and from the shuttle valve, in particular at least partially integrated in the valve slide, or from the, in particular at least 4/2 changeover valve that is partially integrated in the valve spool can be set automatically and dynamically. This allows advantageous damping properties to be achieved. A damping characteristic for shock absorbers can advantageously be achieved which at the same time has high dynamics and low overall leakage.

The valve slide according to the invention, the control valve according to the invention, the vehicle according to the invention and the method according to the invention should not be limited to the application and embodiment described above. In particular, the valve slide according to the invention, the control valve according to the invention, the vehicle according to the invention and the method according to the invention can have a number of individual elements, components, method steps and units that differs from the number specified here in order to fulfill a function described herein.

drawings

Further advantages result from the following description of the drawing. Two exemplary embodiments of the invention are shown in the drawings. The drawings, the description and the claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into further meaningful combinations.

Show it:

Fig. 1 A schematic representation of a vehicle with a bidirectional control valve,

2 shows a schematic section, taken in a first section plane, through the control valve with a hydraulic valve slide through which flow can take place,

3 shows a damping characteristic diagram of the control valve,

4 shows a detail of a further schematic section through the control valve with the valve slide, taken in a second section plane that differs from the first section plane,

5 shows a section of a further schematic section through the control valve with the valve spool, taken in a third section plane that differs from the first section plane and from the second section plane,

6 shows a schematic flow chart of a method for an automatic setting of instantaneous flow directions through the valve slide of the control valve,

7a shows a schematic hydraulic circuit diagram of the control valve according to the invention,

7b shows a schematic hydraulic circuit diagram of a control valve known from the prior art,

8 schematically shows a perspective view of an alternative hydraulic valve slide through which flow can take place for an alternative bidirectional control valve and

9 shows a schematic section through part of the alternative control valve with the alternative valve spool. Description of the exemplary embodiments

FIG. 1 schematically shows a vehicle 70a with a bidirectional control valve 10a. The vehicle 70a is designed as a passenger car. Alternative vehicles with chassis, such as other road vehicles, agricultural vehicles, rail vehicles, aircraft, etc. are also conceivable. The bidirectional control valve 10a is provided for controlling damping characteristics, in particular of shock absorbers (not shown) of the vehicle 70a. The bidirectional control valve 10a according to the invention makes it possible to control a pressure drop at a valve slide 14a of the bidirectional control valve 10a from a volume flow of less than 10 l/min, preferably less than 5 l/min and preferably less than 2 l/min.

FIG. 2 shows a schematic section, taken in a first section plane, through the control valve 10a. The control valve 10a has the valve slide 14a. The valve slide 14a is designed so that it can be flowed through. The valve slide 14a can be flowed through by a pressure fluid of a hydraulic system. The control valve 10a has a first pressure connection 84a (cf. FIG. 4). The control valve 10a has a first tank 66a. The first tank 66a is fluidically connected to the first pressure port 84a. The control valve 10a has a second pressure connection 86a (cf. FIG. 4). The control valve 10a has a second tank 68a. The second tank 68a can be separated from the first tank 66a in a fluid-tight manner. The tanks 66a, 68a can be separated from one another by the valve slide 14a. The second tank 68a is fluidically connected to the second pressure port 86a. The tensile forces and compressive forces that are to be damped by the shock absorber are present at the pressure connections 84a, 86a. For example, shock absorber compression forces produce a pressure acting on the valve spool 14a at the first pressure port 84a and shock absorber tensile forces produce a pressure acting on the valve spool 14a at the second pressure port 86a. When shock absorber compressive forces act on valve spool 14a, second pressure port 86a forms a unpressurized side of the control valve 10a. When shock absorber tensile forces act on the valve slide 14a, the first pressure connection 84a forms an unpressurized side of the control valve 10a. If the pressure applied to the valve slide 14a exceeds a limit value (opening pressure), the valve slide 14a opens a connection between the two pressure ports 84a, 86a. The pressure connections 84a, 86a are designed as openings in a valve housing 88a of the control valve 10a. The valve slide 14a is arranged completely within the valve housing 88a. The valve housing 88a of the control valve 10a, in particular a valve seat element 90a connected to the valve housing 88a, forms a valve seat 24a. The valve slide 14a is intended to be seated sealingly on the valve seat 24a. When the valve slide 14a moves along an intended direction of movement 34a of the valve slide 14a, the valve seat 24a opens and closes. The valve slide 14a is provided to generate a damping of the tensile or compressive forces applied to the control valve 10a depending on its open position. When an applied tensile or compressive force is large enough to lift the valve spool 14a from the valve seat 24a, a pressurized fluid flows between the pressure ports 84a, 86a, thereby dampening the applied tensile or compressive forces. By setting a force with which the valve slide 14a is pressed onto the valve seat 24a, a damping hardness of the control valve 10a, in particular of the chassis damper, can be set. When the valve slide 14a is strongly pressed onto the valve seat 24a, the damping characteristic is hard. When the valve slide 14a is pressed less strongly onto the valve seat 24a, the damping characteristic is soft. The valve slide 14a has a sealing surface 26a. The sealing surface 26a is provided for a (fluid-)tight seating of the valve slide 14a on the valve seat 24a of the control valve 10a.

The control valve 10a has an electromagnet 92a. The electromagnet 92a has a magnetic coil 94a. The electromagnet 92a is provided to generate a force necessary for lifting the valve slide 14a from the valve seat 24a set. Depending on a magnetic field strength generated by the magnetic coil 94a, the force required to lift the valve slide 14a from the valve seat 24a increases. The electromagnet 92a is designed as a reluctance magnet. The electromagnet 92a includes a magnetic core 96a. The magnetic core 96a is largely arranged in an interior of the magnetic coil 94a. The magnet core 96a protrudes in the direction of the valve slide 14a from inside the magnet coil 94a. The control valve 10a has a main armature 98a. The main armature 98a is designed as a magnet armature made of a ferromagnetic material. The main armature 98a is located inside the solenoid coil 94a. The main armature 98a is movably mounted in the interior of the magnetic coil 94a. An air gap 100a of the electromagnet 92a designed as a reluctance magnet is arranged between the main armature 98a and the magnet core 96a. The main armature 98a is pulled in the direction of the magnetic core 96a and/or held in a position close to the magnetic core 96a by the magnetic field of the magnetic coil 94a. The main armature 98a is supported on a side opposite the magnetic core 96a by a compression spring 102a on an upper side of the control valve 10a. The electromagnet 92a has a magnet housing 104a enclosing the magnet coil 94a. The valve housing 88a and the magnet housing 104a are connected to one another in a sealed manner. The control valve 10a, in particular the electromagnet 92a, has a plunger element 106a. The plunger element 106a is fixedly connected to the main anchor 98a or is supported on the main anchor 98a. The tappet element 106a is provided for transmitting a force generated by the main armature 98a to the valve slide 14a. The tappet element 106a protrudes from the inside of the magnetic coil 94a in the direction of the valve spool 14a. The plunger element 106a can be actuated by the magnetic coil 94a. The tappet element 106a is provided for setting a variable damping characteristic of the control valve 10a in an energized (normal) operating state depending on the magnetic field strength generated by the magnetic coil 94a. The control valve 10a has a pressurized fluid reservoir 42a. The volume of the pressurized fluid reservoir 42a can be changed by a movement of the valve slide 14a. The Pressure fluid reservoir 42a can be partially filled and partially emptied by the pressure fluid (eg oil) flowing through the valve slide 14a. The pressurized fluid reservoir 42a is formed separately from the tanks 66a, 68a. With regard to the configuration and functioning of the control valve 10a, reference is also made to the German patent application with the application number 10 2021 134 565.0, the content of which is hereby incorporated in its entirety in this patent application.

Figure 3 shows an example of a damping characteristic diagram 72a of the control valve 10a according to the invention with the valve slide 14a according to the invention, in which a damper speed (in l/min) is plotted on an abscissa 74a and a damping force/pressure (in bar) is plotted on an ordinate 76a. is applied. Here, positive damping forces correspond to compressive forces and negative damping forces correspond to tensile forces. A narrow area with a strong gradient starting from a zero point 78a of the damping characteristic diagram 72a indicates a respective leakage 80a of the control valve 10a in the tension and compression direction. The points at which the gradients become smaller are referred to as opening points 82a, 82'a of the control valve 10a and indicate from when the valve slide 14a and not leaks in the valve slide 14a or other components determine the damping characteristics. The magnitude of the damping force (i.e., the "height" of the solid line) is adjustable by controlling the magnetic field strength of the electromagnet 92a. The solid lines indicate a damping characteristic in the energized (normal) operating state for a specific magnetic field.

FIG. 4 shows a detail of a further schematic section through the control valve 10a, taken in a second section plane that differs from the first section plane. The valve slide 14a can be flowed through. The valve slide 14a is designed as a hydraulic valve slide 14a through which a flow can flow. The valve spool 14a has a hydraulic link valve 12a. The hydraulic linkage valve 12a is integrated into the valve slide 14a. The hydraulic link valve 12a shown in FIG. 4 is a a dual pressure valve 38a is formed. The two-pressure valve 38a has a valve spool 120a which is provided for setting the open position of the two-pressure valve 38a. The hydraulic linkage valve 12a is provided to influence the flow through the valve slide 14a. The hydraulic linkage valve 12a has a first control port 16a. The hydraulic linking valve 12a has a first input 20a. In the case shown in FIG. 4, the first control connection 16a and the first input 20a coincide (in one element). The hydraulic linkage valve 12a has a second control port 18a. The hydraulic linking valve 12a has a second input 36a. In the case shown in FIG. 4, the second control connection 18a and the second input 36a coincide (in one element). The hydraulic linking valve 12a has one (here: exactly one) output 22a. The output 22a is arranged separately from the control terminals 16a, 18a. Depending on the position of the hydraulic linking valve 12a, the output 22a can be opened alternately to one of the inputs 20a, 36a. The two-pressure valve 38a is provided to automatically and dynamically create a valve spool flow connection between the pressure fluid reservoir 42a and only that of the two tanks 66a, 68a which currently has a lower pressure load, in particular which is currently unpressurized.

The first control port 16a is hydraulically connected to a first side 28a of the valve spool 14a. The second control port 18a is hydraulically connected to a second side 30a of the valve slide 14a. The two sides 28a, 30a, with which the control connections 16a, 18a are hydraulically connected, are arranged relative to the valve slide 14a/on the valve slide 14a in such a way that the first side 28a and the second side 30a are connected to one another by the sealing surface 26a of the valve slide 14a (Fluid-tight) can be sealed. The outlet 22a of the hydraulic linking valve 12a of FIG. 4 is hydraulically connected to a third side 32a of the valve spool 14a. The third side 32a of the valve slide 14a is in the intended direction of movement 34a of the Valve spool 14a seen arranged opposite to the sealing surface 26a of the valve spool 14a.

The two-pressure valve 38a is provided to open the input 20a, 36a, which is associated with the control port 16a, 18a with the lower pressure, to the output 22a and/or to keep it open. The valve slide 14a has a flow channel 56a. The flow channel 56a is designed as a recess in the valve slide 14a. The hydraulic linking valve 12a (the two-pressure valve 38a) is assigned to the flow channel 56a. The flow channel 56a comprises three flow sub-channels: a flow sub-channel connected to the first input 20a of the hydraulic linking valve 12a, a flow sub-channel connected to the second input 36a of the hydraulic linking valve 12a, and a flow sub-channel connected to the output 22a of the hydraulic linking valve 12a. The partial flow channels of the flow channel 56a can be designed as bores in the valve slide 14a. The flow channel 56a includes a branch 110a. In the branch 1 10a, three flow sub-channels of the flow channel 56a meet, each of which opens into one of the aforementioned flow sub-channels. The flow channel 56a includes a first flow path 1 12a. The first flow path 112a extends over the branch 110a between the flow sub-channel connected to the first input 20a of the hydraulic linking valve 12a and the flow sub-channel connected to the output 22a of the hydraulic linking valve 12a. The flow channel 56a includes a second flow path 114a. The second flow path 1 14a extends over the branch 1 10a between the flow sub-channel connected to the second input 36a of the hydraulic linking valve 12a and the flow sub-channel connected to the output 22a of the hydraulic linking valve 12a. Both flow paths 1 12a, 1 14a of the flow channel 56a open into the flow sub-channel connected to the output 22a of the hydraulic linkage valve 12a. The Partial flow channel, which starts from the outlet 22a, extends obliquely/at an angle relative to the intended direction of movement 34a of the valve spool 14a.

The outlet 22a of the two-pressure valve 38a is hydraulically connected to a region 44a of the valve spool 14a, which is provided for at least partially delimiting the pressure fluid reservoir 42a of the control valve 10a. The pressure fluid reservoir 42a is intended to be filled and/or emptied when the valve slide 14a moves via one of the flow paths 112a, 114a controlled at least by the two-pressure valve 38a. The pressurized fluid reservoir 42a is defined in part by the valve housing 88a. The pressurized fluid reservoir 42a is formed by interaction of the valve spool 14a and the valve housing 88a. In the state of the two-pressure valve 38a shown by way of example in FIG. 4 , the first flow path 112a is open and the second flow path 114a is closed. In this case, the higher pressure is therefore present at the second control connection 18a.

FIG. 5 shows a detail of a further schematic section through the control valve 10a, taken in a third section plane which differs from the first section plane and from the second section plane. The valve slide 14a has a further hydraulic link valve 54a. The further hydraulic linking valve 54a is designed differently from the hydraulic linking valve 12a. The further hydraulic linking valve 54a differs in a functional principle from the hydraulic linking valve 12a. The additional hydraulic linkage valve 54a is integrated into the valve slide 14a. The further hydraulic linking valve 54a is formed separately from the hydraulic linking valve 12a. The additional hydraulic linkage valve 54a is also provided for influencing a flow through the valve slide 14a. The additional hydraulic linkage valve 54a shown in FIG. 5 is designed as a shuttle valve 48a. The further hydraulic Linkage valve 54a has a first control port 16'a. The additional hydraulic linkage valve 54a has a first input 20'a. In the case shown in FIG. 5, the first control connection 16'a and the first input 20'a coincide (in one element). The additional hydraulic linkage valve 54a has a second control port 18'a. The additional hydraulic linkage valve 54a has a second input 36'a. In the case shown in FIG. 5, the second control connection 18'a and the second input 36'a coincide (in one element). The additional hydraulic linkage valve 54a has one (here: exactly one) output 22'a. The output 22'a is arranged separately from the control connections 16'a, 18'a. The outlet 22'a can be opened alternately to one of the inlets 20'a, 36'a, depending on the position of the further hydraulic linking valve 54a. The shuttle valve 48a has a valve element 124a (shown here as a valve ball), which is provided for setting the open position of the shuttle valve 48a.

The first control port 16'a of the additional hydraulic linkage valve 54a is hydraulically connected to the first side 28a of the valve slide 14a. The second control port 18'a of the additional hydraulic linkage valve 54a is hydraulically connected to the second side 30a of the valve slide 14a. The two sides 28a, 30a, with which the control connections 16'a, 18'a of the further hydraulic linking valve 54a are hydraulically connected, are arranged relative to the valve slide 14a/on the valve slide 14a in such a way that the first side 28a and the second side 30a can be sealed to one another (fluid-tight) by the sealing surface 26a of the valve slide 14a. The outlet 22'a of the further hydraulic linkage valve 54a of FIG. 4 is hydraulically connected to the third side 32a of the valve slide 14a. The outlet 22'a of the shuttle valve 48a is hydraulic with a hydraulic effective area 50a of the valve spool 14a, which is formed on the side 28a, 30a of the valve spool 14a on which the shuttle valve 48a is currently open , opposite. The opposing hydraulic active surfaces 50a, 52a are different in size (for further explanations see also the disclosure of the German patent application filed with the application number 10 2021 134 565.0). The outlet 22'a of the shuttle valve 48a is different and designed and arranged separately from the outlet 22a of the two-pressure valve 38a. The inputs 20'a, 36'a of the shuttle valve 48a are each designed and arranged differently and separately from the inputs 20a, 36a of the two-pressure valve 38a.

The shuttle valve 48a is provided to open the input 20'a, 36'a, to which the control connection 16'a, 18'a with the higher pressure is assigned, to the output 22'a and/or to keep it open. The valve slide 14a has a further flow channel 58a. The further flow channel 58a is designed as a recess in the valve slide 14a. The additional hydraulic linking valve 54a (the shuttle valve 48a) is assigned to the additional flow channel 58a. The two flow channels 56a, 58a are completely separate from one another. The two flow channels 56a, 58a are designed without connection to one another. The further flow channel 58a comprises three flow sub-channels: a flow sub-channel connected to the first input 20'a of the further hydraulic link valve 54a, a flow sub-channel connected to the second input 36'a of the further hydraulic link valve 54a and a flow sub-channel connected to the outlet 22'a of the further hydraulic Linkage valve 54a connected flow sub-channel. The further flow channel 58a includes a further branch 46a. In the further branch 46a, three flow sub-channels of the further flow channel 58a meet, which each open into one of the aforementioned flow sub-channels. The further flow channel 58a includes a third flow path 108a. The third through-flow path 108a extends across the branch 46a between the partial flow channel connected to the first input 20'a of the further hydraulic linking valve 54a and the partial flow channel connected to the output 22'a of the further hydraulic linking valve 54a. The other Flow channel 58a includes a fourth flow path 116a. The fourth through-flow path 116a extends across the branch 46a between the partial flow channel connected to the second input 36'a of the further hydraulic linking valve 54a and the partial flow channel connected to the output 22'a of the further hydraulic linking valve 54a. Both flow paths 108a, 116a of the further flow channel 58a open into the flow sub-channel connected to the outlet 22'a of the further hydraulic linkage valve 54a. The partial flow channel, which starts from the outlet 22'a of the further hydraulic linkage valve 54a, extends parallel to the intended direction of movement 34a of the valve slide 14a.

FIG. 6 shows a schematic flowchart of a method for an automatic setting of instantaneous flow directions through the flow-through hydraulic valve slide 14a of the control valve 10a. In the method, an instantaneous flow direction is automatically and dynamically adjusted by the two-pressure valve 38a that is at least partially integrated in the valve slide 14a and by the shuttle valve 48a that is at least partially integrated in the valve slide 14a. Alternatively, instead of the combination of two-pressure valve 38a and shuttle valve 48a, a 4/2 shuttle valve 60b integrated at least partially in valve slide 14b, as shown in the following FIGS. 8 and 9, can also be used. The behavior of the control valve 10a when a pressure to be damped is applied to the second tank 68a is described below by way of example and schematically (see also FIGS. 4 and 5). In at least one method step 118a, the two-pressure valve 38a is actuated by the applied pressure in such a way that the valve slide 120a of the two-pressure valve 38a is pushed by the applied pressure into a position in which the valve slide 120a of the two-pressure valve 38a opens the first flow path 112a and the second flow path 114a closed. This establishes a fluidic connection between the currently unpressurized first tank 66a and the pressurized fluid reservoir 42a. The Pressure fluid reservoir 42a could be filled or emptied without resistance when the valve slide 14a moves (for example, if the applied pressure exceeds the limit value of the opening point 82a). In at least one further method step 122a, valve element 124a of shuttle valve 48a is (substantially simultaneously) pushed by the applied pressure into a position in which valve element 124a of shuttle valve 48a closes third flow path 108a and opens fourth flow path 116a. This establishes a fluid connection between the second tank 66a, on which the pressure is applied, and the hydraulic effective surface 50a of the valve slide 14a. The applied pressure is thus forwarded to the hydraulic effective surface 50a of the valve slide 14a. In at least one further method step 126a, a resistance force of the valve slide 14a against lifting of its sealing surface 26a from the valve seat 24a is set by selecting an energization of the magnetic coil 94a of the electromagnet 92a. In at least one further method step 128a, if the limit value given by the opening point 82a is exceeded by the applied pressure, the valve slide 14a is lifted from the valve seat 24a, so that pressurized fluid can flow from the second tank 68a into the first tank 66a (or vice versa). This creates/achieves a damping of the applied pressure.

FIG. 7a shows a schematic hydraulic circuit diagram of the control valve 10a according to the invention. Apart from the hydraulic linkage valve 12a and apart from the further hydraulic linkage valve 54a, the through-flow hydraulic valve slide 14a has an orifice-free design 64a. FIG. 7b shows a schematic hydraulic circuit diagram of a control valve known from the prior art with a plurality of orifices 130a and check valves 132a.

A further exemplary embodiment of the invention is shown in FIGS. The following descriptions and the drawings are essentially limited to the differences between the exemplary embodiments, where With regard to components with the same designation, in particular with regard to components with the same reference symbols, reference can in principle also be made to the drawings and/or the description of the other exemplary embodiments, in particular FIGS. 1 to 7a. To distinguish between the exemplary embodiments, the letter a follows the reference number of the exemplary embodiment in FIGS. 1 to 7b. In the exemplary embodiments of FIGS. 8 and 9, the letter a has been replaced by the letter b.

FIG. 8 schematically shows a perspective representation of an alternative hydraulic valve slide 14b through which flow can take place. The alternative valve slide 14b can be used in a control valve 10b which, apart from the valve slide 14b, is identical to the control valve 10a already described. The alternative valve spool 14b fulfills the same function as the valve spool 14a already described. The alternative valve spool 14a has an alternative hydraulic linkage valve 12b. The alternative hydraulic linking valve 12b is integrated into the valve spool 14b. The alternative hydraulic link valve 12b is designed as a single valve. The single valve is designed as a 4/2 shuttle valve 60b. The 4/2 shuttle valve 60b combines the function of a shuttle valve with the function of a two-pressure valve in one valve.

FIG. 9 shows a schematic section through part of the alternative valve slide 14b and through the alternative hydraulic linkage valve 12b designed as a 4/2 shuttle valve 60b. The 4/2 shuttle valve 60b has a first control port 16b. The 4/2 shuttle valve 60b has a first input 20b. In the case shown in FIG. 9, the first control connection 16b and the first input 20b coincide (in one element). The 4/2 shuttle valve 60b has a second control port 18b. The 4/2 shuttle valve 60b has a second input 36b. The second inlet 36b is fluidically connected to a second tank 68b. The external pressure of the shock absorber can be present at the second input 36b. In the case shown in FIG. 9, the second control connection is 18b and the second input 36b separated / different from each other. The 4/2 shuttle valve 60b has an outlet 22b. The output 22b is arranged/designed separately from the control connections 16b, 18b and the inputs 20b, 36b. Depending on the setting of the 4/2-way shuttle valve 60b, the outlet 22b can be opened alternately to one of the inlets 20b, 36b. The 4/2 shuttle valve 60b has a further outlet 40b. The further output 40b is arranged/designed separately from the control connections 16b, 18b and the inputs 20b, 36b. Depending on the setting of the 4/2-way shuttle valve 60b, the other outlet 40b can be opened to one of the inlets 20b, 36b.

The 4/2 shuttle valve 60b is provided to open the input 20b, 36b, to which the control connection 16b, 18b with the lower pressure is assigned, to the output 22b and/or to keep it open. The 4/2-way shuttle valve 60b is provided for simultaneously opening the input 20b, 36b, to which the control port 16b, 18b is associated with the higher pressure, to the further output 40b and/or keeping it open. The valve slide 14b has a flow channel 56b and a further flow channel 58b. The 4/2 shuttle valve 60b is assigned to both flow channels 56b, 58b. The flow channel 56b includes a first flow path 112b. The first flow path 112b extends between a flow sub-channel connected to the first input 20b of the 4/2 changeover valve 60b and to a first tank 66b of the control valve 10b and to the output 22b of the 4/2 changeover valve 60b and to the first tank 66b opposite hydraulic effective surface 50b connected flow sub-channel. The flow channel 56b includes a second flow path 114b. The second flow path 114b extends between a partial flow channel connected to the second inlet 36b of the 4/2 shuttle valve 60b and to the second tank 68b of the control valve 10b and a flow channel connected to the outlet 22b of the 4/2 shuttle valve 60b and to the hydraulic effective surface 50b connected flow sub-channel. Both flow paths 112b, 114b of the Flow channel 56b thus open into the flow sub-channel connected to the outlet 22b of the 4/2 shuttle valve 60b.

The further flow channel 58b includes a third flow path 108b. The third flow path 108b extends between a flow part channel connected to the first input 20b of the 4/2 changeover valve 60b and to the first tank 66b of the control valve 10b and a flow part channel connected to the second output 40b of the 4/2 changeover valve 60b and to a pressurized fluid Reservoir 42b of the control valve 10b connected flow sub-channel. The further flow channel 58b includes a fourth flow path 116b. The fourth flow path 116b extends between a flow part channel connected to the second input 36b of the 4/2 changeover valve 60b and to the second tank 68b of the control valve 10b and to the second output 40b of the 4/2 changeover valve 60b and to the pressure fluid Reservoir 42b of the control valve 10b connected flow sub-channel. Both through-flow paths 108b, 116b of the further flow channel 58b thus open into the flow sub-channel connected to the further outlet 40b of the 4/2 changeover valve 60b.

The 4/2 shuttle valve 60b is thus provided to open the input 20b, 36b, which is associated with the control port 16b, 18b of the two control ports 16b, 18b, at which the higher pressure is present, to the output 22b and/or open to keep and at the same time the input 20b, 36b, which is associated with the control port 16b, 18b of the two control ports 16b, 18b, at which the lower pressure is applied, open to the further output 40b and/or keep it open.

The 4/2 shuttle valve 60b includes a first valve portion 134b and a second valve portion 136b. The first valve part 134b is sealingly introduced into a recess 140b of the valve slide 14b. The first valve part 134b forms five areas 142b, 144b, 146b, 148b, 150b (first area 142b, second area 144b, third area 146b, fourth area 148b, fifth area 150b). The areas 142b, 144b, 146b, 148b, 150b can each be sealed to one another (depending on a position of the second valve part 136b) and/or optionally (depending on a position of the second valve part 136b) with one of the further areas 142b, 144b, 146b, 148b, 150b linkable. The first area 142b is arranged in the axial direction 158b of the 4/2 shuttle valve 60b outside the 4/2 shuttle valve 60b on a first axial side 152b of the first valve part 134b. The second valve part 136b is movably mounted in the axial direction 158b. The first region 142b is in fluid communication with the first tank 66b. The first area 142b is sealed off from the other areas 144b, 146b, 148b, 150b on the outer circumference of the 4/2 shuttle valve 60b by a first seal 156b of the first valve part 134b. The second region 144b is fluidically connected to the hydraulic effective surface 50b. The second area 144b is on the outer circumference of the 4/2 shuttle valve 60b on one side through the first seal 156b to the first area 142b and on an opposite side through a second seal 160b of the first valve part 134b to the further areas 146b, 148b, 150b sealed. The third area 146b is in fluid communication with the second tank 68b. The third portion 146b is on the outer periphery of the 4/2 shuttle valve 60b on one side through the second seal 160b to the first portion 142b and the second portion 144b and on an opposite side through a third seal 162b of the first valve part 134b to the other portions 148b, 150b sealed. The fourth region 148b is in fluid communication with the pressurized fluid reservoir 42b. The fourth portion 148b is on the outer periphery of the 4/2 shuttle valve 60b on one side by the third seal 162b to the first portion 142b, the second portion 144b and the third portion 146b and on an opposite side by a fourth seal 164b of the first valve part 134b sealed to the fifth region 150b. The fifth area 150b is arranged in the axial direction 158b of the 4/2 shuttle valve 60b outside the 4/2 shuttle valve 60b on a second axial side 154b of the first valve part 134b. The fifth area 150b is fluidically connected to the second tank 68b. The fifth area 150b is on the outer circumference of the 4/2 shuttle valve 60b sealed by the fourth seal 164b of the first valve part 134b to the other areas 142b, 144b, 146b, 148b.

The second valve part 136b is arranged inside the first valve part 134b. The second valve part 136b is arranged axially movable in the first valve part 134b. The second valve part 136b sealingly slides within a recess 138b of the first valve part 134b. The second valve part 136b forms a linkage valve valve slide 62b through which flow can flow at least in sections. The second valve part 136b is intended to be moved back and forth between a first valve position 166b and a second valve position 168b. In FIG. 9, the second valve part 136b is in the first valve position 166b, while the second valve position 168b is indicated only by dashed lines. The second valve part 136b is intended to be brought into the respective valve position 166b, 168b by the pressures present at the control connections 16b, 18b. For this purpose, the second valve part 136b has a first pressure application surface 170b and a second pressure application surface 172b. The first pressure application surface 170b is provided for applying a pressure from the first tank 66b/from the first control port 16b. The second pressure application surface 172b is provided for applying a pressure from the second tank 68b/from the second control port 18b. The flow-through linking valve valve spool 62b has a flow-through recess 174b. The through-flow recess 174b can be filled with the pressure fluid/through which the pressure fluid can flow. The through-flow recess 174b is open axially toward the first axial side 152b. The throughflow recess 174b is closed axially towards the second axial side 154b. The through-flow recess 174b has at least one inflow and/or outflow opening 178b in an end region 176b of the second valve part 136b located on the second axial side 154b, which allows pressure fluid to flow in and/or out in a direction 180b radial to the axial direction 158b. The second valve part 136b is free of further inlets and/or outlets along the remainder of its extension in the axial direction 158b outflow openings. The first pressure application surface 170b and the second pressure application surface 172b are both arranged in the same end region 176b of the second valve part 136b, in particular in the end region 176b of the second valve part 136b lying on the second axial side 154b. The first pressure application surface 170b is arranged inside the through-flow recess 174b of the second valve part 136b. The second pressure application surface 172b is arranged outside of the throughflow recess 174b of the second valve part 136b. The second pressure application surface 172b is arranged on an axially outer surface of the second valve part 136b.

In the second region 144b, the first valve part 134b has at least one inflow and/or outflow opening 182b on an outer circumference, in particular one lying in the radial direction 180b with respect to the axial direction 158b, which provides a fluidic connection from one interior space of the first valve part 134b to the other hydraulic effective surface 54b allowed. The first valve part 134b has at least one inflow and/or outflow opening 184b in the third region 146b on an outer circumference, in particular lying in the radial direction 180b with respect to the axial direction 158b, which provides a fluidic connection from the interior of the first valve part 134b to the second Tank 68b allowed. In fourth region 148b, first valve part 134b has at least one inflow and/or outflow opening 186b on an outer circumference, in particular one lying in radial direction 180b with respect to axial direction 158b, which provides a fluidic connection from the interior of first valve part 134b to the pressurized fluid -Reservoir 42b allowed. The first area 142b and the fifth area 150b are each connected to the interior of the first valve part 134b by axial inflow and/or outflow openings 188b, 190b.

In the first valve position 166b, the first region 142b is fluidically connected to the second region 144b. In the first valve position 166b, the third region 146b is fluidically connected to the fourth region 148b. In the first valve position 166b, the fifth region 150b is fluidic not connected to any of the other areas 142b, 144b, 146b, 148b. In the first valve position 166b, the first area 142b and the second area 144b are fluidically separated from the further areas 146b, 148b, 150b. In the first valve position 166b, the third area 146b and the fourth area 148b are fluidically separated from the further areas 142b, 144b, 150b.

In the second valve position 168b, the first region 142b is fluidically connected to the fourth region 148b. In the second valve position 168b, the second region 144b is fluidically connected to the third region 146b. In the second valve position 168b, the fifth region 150b is fluidically connected to none of the further regions 142b, 144b, 146b, 148b. In the second valve position 168b, the volume of the fifth region 150b is greater than in the first valve position 166b. In the second valve position 168b, the first area 142b and the fourth area 148b are fluidically separated from the further areas 144b, 146b, 150b. In the second valve position 168b, the second area 144b and the third area 146b are fluidically separated from the further areas 142b, 148b, 150b.

Reference sign

10 control valve

12 linkage valve

14 valve spool

16 First control connection

18 Second control connection

20 First entrance

22 exit

24 valve seat

26 sealing surface

28 First page

30 second page

32 Third page

34 direction of movement

36 Second entrance

38 dual pressure valve

40 Another exit

42 pressurized fluid reservoir

44 area

46 Further branching

48 shuttle valve

50 hydraulic effective area

52 More effective hydraulic area

54 Another linking valve

56 flow channel

58 Another flow channel

60 4/2 shuttle valve

62 linkage valve spool

64 Glare-free design

66 First tank second tank

vehicle

Damping Characteristics Diagram

abscissa

ordinate

zero point

leakage

opening point

First pressure connection

Second pressure port

valve body

valve seat element

electromagnet

magnetic coil

magnetic core

main anchor

air gap

compression spring

magnet case

plunger element

Third flow path

branch

First flow path

Second flow path

Fourth flow path

process step

valve spool

process step

valve element

process step

process step cover

check valve

First valve part

Second valve part

recess

recess

First area

second area

third area

fourth area

fifth area

First axial side

Second axial side

First seal

axial direction

Second seal

Third seal

Fourth Seal

First valve position

Second valve position

First pressure attack surface

Second pressure attack surface

through-flow recess

end area

Inflow and/or outflow opening

radial direction

Inflow and/or outflow opening

Inflow and/or outflow opening

Inflow and/or outflow opening

Axial inflow and/or outflow opening

Axial inflow and/or outflow opening

Claims

Claims Flow-through hydraulic valve slide (14a-b), in particular for a control valve (10a-b) for controlling damping characteristics of shock absorbers, with at least one hydraulic linkage valve (12a-b) for influencing a flow through the valve slide (14a-b), wherein the hydraulic linkage valve (12a-b) at least one first control port (16a-b), at least one second control port (18a-b), at least one input (20a-b, 36a-b) and at least one output (22a-b, 40b) , which can be opened at least to the entrance (20a-b) in an exchangeable manner. Flow-through hydraulic valve slide (14a-b) according to Claim 1, characterized by a sealing surface (26a-b) provided for seating tightly on a valve seat (24a-b) of the control valve (10a-b), the first control connection (16a-b ) is hydraulically connected to a first side (28a-b) of the valve spool (14a-b), the second control port (18a-b) being hydraulically connected to a second side (30a-b) of the valve spool (14a-b), and wherein the two sides (28a-b, 30a-b) to which the control connections (16a-b, 18a-b) are hydraulically connected are arranged on the valve slide (14a-b) in such a way that the first side (28a -b) and the second side (30a-b) can be sealed to one another by the sealing surface (26a-b). Flow-through hydraulic valve slide (14a-b) according to Claim 2, characterized in that the outlet (22a-b) is hydraulically connected to a third side (32a-b) of the valve slide (14a-b) which, in an intended direction of movement (34a -b) of the valve slide (14a-b) is arranged opposite to the sealing surface (26a-b). Flow-through hydraulic valve slide (14a) according to one of the preceding claims, characterized in that the hydraulic linking valve (12a) is designed as a dual-pressure valve (38a) which is provided in particular to connect the input (20a, 36a) to which the control connection (16a , 18a) associated with the lower pressure to open to the outlet (22a) and/or to keep it open. Flow-through hydraulic valve slide (14a) according to Claim 4, characterized in that the outlet (22a) of the two-pressure valve (38a) is connected hydraulically to a region (44a) of the valve slide ( 14a), the pressure fluid reservoir (42a) being intended in particular to be filled and/or emptied when the valve slide (14a) moves via a flow path (112a, 114a) controlled at least by the dual-pressure valve (38a). Flow-through hydraulic valve slide (14a) according to one of the preceding claims, characterized in that the hydraulic linking valve (12a) is designed as a shuttle valve (48a), which is provided in particular to the input (20'a, 36'a), the the control port (16'a, 18'a) is assigned to the higher pressure, to open to the outlet (22'a) and/or to keep it open. 7. Flow-through hydraulic valve slide (14a) according to Claim 6, characterized in that the outlet (22'a) of the shuttle valve (48a) is hydraulically connected to a hydraulic active surface (50a) which is connected to a further hydraulic active surface (52a) which is on the side (28a, 30a) of the valve spool (14a) is formed, to which the shuttle valve (48a) is currently open, opposite. 8. Flow-through hydraulic valve slide (14a) according to claim 7, characterized in that the opposite active hydraulic surfaces (50a, 52a) are of different sizes. 9. Flow-through hydraulic valve slide (14a) according to one of the preceding claims, characterized by at least one further hydraulic linkage valve (54a), in particular one that differs from the hydraulic linkage valve (12a) in a functional principle, for influencing a flow through the valve slide (14a), wherein the additional hydraulic linkage valve (54a) has at least one first control port (16a, 16'a) and at least one second control port (18a, 18'a). 10. Flow-through hydraulic valve slide (14a) according to claim 9, characterized in that the hydraulic linking valve (12a) is designed as a dual-pressure valve (38a) and that the further hydraulic linking valve (54a) is designed as a shuttle valve (48a). Flow-through hydraulic valve slide (14a) according to Claim 9 or 10, characterized in that the hydraulic linking valve (12a) is assigned to a flow channel (56a) at least partially formed by the valve slide (14a) and that the further hydraulic linking valve (54a) is connected to a flow channel (56a) formed by the Valve slide (14a) is associated with an at least partially formed further flow channel (58a), the two flow channels (56a, 58a) being completely separate from one another, in particular without being connected to one another. Flow-through hydraulic valve slide (14b) according to one of Claims 1 to 8, characterized in that the hydraulic linkage valve (12b) is designed as a single valve which has at least one further outlet (40b) and which has the function of a shuttle valve with the function of a Two-pressure valve combined in one valve. Flow-through hydraulic valve slide (14b) according to Claim 12, characterized in that the individual valve is designed as a 4/2 shuttle valve (60b) which is provided for the purpose of connecting the inlet (20b, 36b) to the control connection (16b, 18b ) of the two control connections (16b, 18b), to which a higher pressure is applied, is assigned to the outlet (22b) and/or to keep it open and at the same time the inlet (20b, 36b), which is connected to the control connection (16b, 18b ) of the two control connections (16b, 18b), to which a lower pressure is applied, is assigned to open and/or keep open to the further outlet (40b). 14. Flow-through hydraulic valve slide (14b) according to claim 12 or 13, characterized in that the hydraulic linking valve (12b) designed as a 4/2 shuttle valve (60b) has a flow-through linking valve valve slide (62b) at least in sections. 15. Flow-through hydraulic valve slide (14a-b) according to one of the preceding claims, characterized by a design (64a-b) without an orifice, in particular apart from the hydraulic linkage valve (12a-b) and/or apart from the further hydraulic linkage valve (54a). ). 16. Bidirectional control valve (10a-b) for controlling damping characteristics, in particular of shock absorbers, with a flow-through hydraulic valve slide (14a-b) according to one of the preceding claims. 17. Bidirectional control valve (10a-b) according to claim 16, characterized by reaching a controllability of a pressure drop at the valve slide (14a-b) from a volume flow of less than 10 l / min, preferably less than 5 l / min and preferably less than 2L/min. Bidirectional control valve (10a) according to Claim 16 or 17, having a first tank (66a) and having a second tank (68a) which can be separated from the first tank (66a) by the valve slide (14a), characterized by a movement of the valve slide ( 14a) variable-volume pressurized fluid reservoir (42a) configured separately from the tanks (66a, 68a), which can be partially filled and/or partially emptied by flowing through the valve slide (14a), the hydraulic linkage valve configured as a dual-pressure valve (38a). (12a) is provided to automatically and dynamically create a valve slide flow connection between the pressure fluid reservoir (42a) and only that of the two tanks (66a, 68a) which currently has a lower pressure load, in particular which is currently pressureless . Vehicle (70a) with a bidirectional control valve (10a) according to one of Claims 16 to 18. Method for an automatic setting of instantaneous flow directions through flow-through valve slide (14a-b), in particular with a flow-through hydraulic valve slide (14a-b) according to one of Claims 1 to 15 and/or with a control valve (10a-b) according to one of Claims 16 to 18, characterized in that the instantaneous flow directions are controlled by a dual-pressure valve (38a), in particular at least partially integrated in the valve slide (14a), and by a shuttle valve (48a) that is in particular at least partially integrated in the valve slide (14a) or by a 4/2 shuttle valve (60b) that is in particular at least partially integrated in the valve slide (14b).